Fluid operated power transmitter



June 12, 1945. w. JASTRZEBSKI FLUID OPERATED POWER TRANSMITTER Filed Sept. 22, 1942 7 Sheets-Sheet l u fioya.

June 12, 1945.

W. JASTRZEBSK! FLUID OPERATED POWER TRANSMITTER Filed Sept. 22, 1942 7 Sheets-Sheet 2 June 1945- w. JASTRZEBSKI FLUID OPERATED POWER TRANSMITTER Filed Sept. 22, 1942 7 Sheets-Sheet 5 mv WN IIHIII 1 fiiorneya June 12, 1945. w. JASTRZEBSKI FLUID OPERATED POWER TRANSMITTER 7 Sheets-Shed 4 Filed Sept. 22, 1942 June 12, 1945.

W. JASTRZEBSKI FLUID OPERATED POWER TRANSMITTER Filed Sept. 22'. 1942 '7 Sheets-Sheet 5 A AW/ June 12, 1945. w JASTRZEBSKI 2,377,886

RATED POWER TRANSMITTER Filed Sept. 22, 1942 7 Sheets-Sheet 6 25 1 A? [midi J01? A W w m'wi l qiw fitam@a W. JASTRZEBSKI FLUID OPERATED POWER TRANSMITTER June 12 1945.

Filed Sept. 22, 1942 7 Sheets-Sheet '7 5 5 1 -v A A Patented June 12, 1945 FLUID OPERATED POWER TRANSMITTER Wincenty Jastrzebski, Alx-les-Bains, France;

vested in the Allen Property Custodian Application September 22, 1942, Serial No. 459,200

In France December 15, 1941 8 Claims.

Hydraulic change. speed gears are already known wherein the change of gear. ratio from a driving shaft to a driven shaft is obtained by increasing or decreasing the quantity of a liquid force by a pump operatively connected to one of said shafts and derived from another pump I operatively connected to the other shaft. With such a structure, when it is desired to increase the speed of the driven shaft, a larger quantity of liquid .must be displaced from one pump into the other.

It is an object of the present invention to provide as an improvement and development of the aforesaid type of hydraulic change speed gear a novel fluid operated apparatus utilizable as a power transmitter either for imparting to a driven shaft selectively any one of an unlimited number of different speeds from a driving shaft or else as a change speed power transmitter permitting the impulse from a driving shaft to be imparted without any substantial loss of energy to a driven shaft with several different gearing ratios and also a reverse drive to be obtained.

Another object of the invention is to provide a power transmitter utilizable for miscellaneous purposes whenever the speed of a driven mechanical member requires to be varied and having a simple structure ensuring an inexpensive operation because it functions by controlling a member which regulates the circulation of a liquid. such as oil, filling the transmitter chamber capacity, said circulation resulting from the resistance which checks the motion of the driven shaft with respect to the motion to be imparted thereto by the drivingshaft, to each reduction of the mass of circulating liquid corresponding an increase of the driven shaft speed, i. e. a decrease of the ratio between the respective speeds of both shafts. A

Yet another object of the invention; is more specifically to provide an oil operated power' transmitter comprising span of revoluble coaxial elements movable with respect to each other and so interengased as to delineate chambers whose total volume is constant while their partial volumes vary when one of said elements is moved with respect to the other responsive to varying resistances, said power transmitter enabling a number of diflerent rates of speed to be imparted to a driven shaft from a driving shaft revolving at uniform speed. A further object of the invention is to provide a novel fluid operated power transmitter as aforesaid made up of a small number or simple and rugged members affording the entire structure good operating conditions and proper durability.

A still further object of the invention is to provide a novel fluid operated power transmitter as aforesaid having a better kinetic efliclency than similar fluid operated appliances devised heretofore and so constructed as to permit a direct drive transmission without any relative displacement of.. members and without any liquid (oil) circulation.

With these and such other objects in view as will incidentally appear hereafter, the invention comprises more particularly the novel construction, combination and arrangements of parts that will be now described in detail with reference to the accompanyingdiagrammatic sheets of drawings exemplifying several embodiments of the same and forming a part of the present disclosure.

In the drawings:

Figure l is a plan view of the entire power transmitter, assuming the semi-circular outer wall to have been removed to disclose location of internal members.

"Figure 2 is a sectional view on the line 2--2 of Fig. 3, assuming one of the shafts to have been rotated 180 with respect to the other shaft.

Figure, 3 is a transverse sectional view on the line 33 of Fig. 2.

Figure 4 is a fragmentary sectional view on the line it of Fig. 3, assuming the set of movable partitions to be omitted.

Figures 5 and 6 are respectively an end view aind a top plan view of a set of movable partit ons.

Figure 7 is a longitudinal sectional view on the line l'-'i of Fig. 8 showing amodifled construction of the transmitter.

Figure 8 is a transverse sectional view on the line 8-8 of Fig. 'l.

Figures 9 and 10, are respectively a top plan view and an elevational view of the movable partition embodied in the modified construction shown in Fig. 7. T

Figure 11 is a longitudinal sectional view on the line III-ll of Figs. 12, 13, 14 and 15 of a power transmitter forming an entire gear box according to the invention.

Figures 12, l3, l4 and 15 are respectively transl verse sectional views along lines l2--i2, l3-l3,

suming the casing to be omitted and after a rotation of 90 about its axis and in section along the line |6c-| 8c of Fig. 16b.

Figures 17, 18 and 19 are views of the movable artition which is visible in Fig. 15 shown respectively in elevational, end and top plan views.

Figures 200., 21a, 22a, 23a, 20b, 21b, 22b and 23b are transverse sectional views of the cylindrical valve taken respectively along the lines 20a20a, 2|a-2|a, 22a-22a, 230-430, Zoo-20b, 2|b--2|b, 22b--22b and 23b-23b of Fig. 11 in positions corresponding to the line |2-|2 of Fig. 11 for the sections bearing the reference a and to the line ||5 of Fig. 11 for the sections bearing the reference b, said positions being occupied after such displacements as are effected to provide idle run, first speed, second speed and reverse respectively.

Figure 24 is an explanatory view setting forth the operation of the power transmitter resulting from the superposition of the sectional views shown by Figs. 12 and 15.

Figure 25 is a longitudinal sectional view of a further constructional modification of a power transmitter according to the invention.

Figures 26, 27 and 28 are transverse sectional views respectively taken along lines 26-28, 21-21 and 28-28 of Fig. 25.

Figure 29 is a separate view of the cylindrical valve, its casing being shown in section.

Figures 30, 31 and 32 are views of the movable partition visible in Fig. 27 taken respectively in end view, in top plan view and in lower plan view.

Figures 33a, 34a, 35a, 36a, 37a, 33b, 34b, 35b, 36b, and 37b are transverse sectional views of the cylindrical valve taken respectively along the lines 33a33a, 34a-34a, 35a-35a, 36a36a, flat-31a, 33b-33b, 3422-341), 35b-35b, 3611-362) and 3lb-3'|b of Fig. 25 in the positions corresponding to 2626 of said figure for sections referenced by a and to 21-21 of the same figure for sections referenced by D, such positions being those assumed after the displacements effected to obtain the idle run, the first speed, the second speed, the third speed and the reverse respectively.

Figure 38 is a diagrammatic isometric view, showing an essential part of the power transmitter according to the invention.

Figure 39 is an explanatory diagram facilitating proper understanding of the power transmitter operation.

As illustrated, the change speed power transmitter is interposed between a shaft 2 (Figs. 1, 2 and 38) which may be and will be termed hereafter a driving shaft and a shaft 5 which may be and will be termed hereafter a driven shaft. Said shaft 5 has a stub extension I which projects into a chamber 8 defined in a peripherally cylindrical casing 9 rigid with the driving shaft 2. The end surfaces of said chamber are constituted by a pair of plates I0, I forming the end closures of the casing 9. The inner surfaces of the plates IO, II have arcuate sinusoidal outlines substantially as shown in Fig. 39 and extend in parallelism.

A surface having such an arcuate outline is generated by a straight line such as ab extending at right angles to the axis of the shaft 2 (Fig. 1) and to which is imparted lengthwise of said axis a sinusoidal motion whose amplitude bears a certain ratio with the extreme degree of unevenness of the plate surface.

Between the sinusoidally undulated surfaces of the plates IO, N is slidably interposed a partition comprising a single element |2 (Fig. 38) parallel to the generatrix ab or a pair of juxtaposed elements I211, I211 (Figs. 1, 5 and 6). Said partition is adapted alternatively to slide between said undulated plates while providing a fluidtight seal between them and also between the casing 9 and the driven shaft 5.

The driven shaft 5 carries a circular diskshaped divider l3 having a thickness equal to the interval (Fig. 39) between planes at right angles to its axis and tangent to the crests or uppermost points of the undulated surfaces of the plates I0, I I. The disk l3 provides fluid tightness along its lines of contact and splits the chamber 8 into a pair of compartments. Said disk l3 has a radial notch It in which is snugly received the partition I2 which is freely slidable therein parallel to the axis of the driven shaft 5 and divides in turn each compartment into a pair of subcompartments.

Communication is provided between both faces I5, l6 of the partition l2 (Fig. 3) b channels l1, l8, I9, 20 in the disk l3. The circulation of the fluid through said channels may be throttled and, if required, fully closed off lby operating primary valve means such as a cock 2| which is movably housed in a central recess 22 parallel to the axis of the driven shaft 5 and separates the channels l8, l9 from each other.

The operation of the power transmitter will be clearly understood from Fig. 39. An examination of this diagram shows that the sub-compartments 5|, 52 defined on opposite sides of the disk i3 and to the right of the partition l2 communicate through a port 53 formed in the right hand face of said partition while the sub-compartments 54, 55 also defined on opposite sides of the disk l3 but to the left of the partition l2 similarly communicate with each other through a port 56 formed in the left hand face of said partition. The longitudinal ports 53, 56 are interconnected by a transverse port 59 whose sectional area is controlled -by secondary valve means such as a cock 6|.

Assuming the shaft 2 to rotatably drive the plates I0, I in the direction indicated by the arrow 29, it will be understood that the action of their undulated surfaces tends to reduce the volume of the sub-compartments 5|, 52 in proportion as their lines of contact 51, 58 with the disk I3 are moved toward the partition I2. This reduction of volume is obviously accompanied by an increase of pressure of the fluid which fills said sub-compartments and which has a tendency to leak out through the ports 53, 59 and 56 into the sub-compartments 54, 55 whose volume gradually increases exactly in terms of the extent 'of gradual reduction of the volume of the sub-compartments 5|, 52.

Assuming all the sub-compartments to be filled with oil or an equivalent liquid, a circulatory motion is imparted to the oil in the direction shown by the arrow 24 (Fig. 3) from the sub-compartments situated on one side of the partition |2 to those situated on the opposite side.

If now by means of the cock 6| (Fig. 39) the port 59 is fully closed, the flow of oil is intercepted therethrough. As a result of this, there is created inside the sub-compartments 5|, 52 an oil overpressure which at once reacts against the partition l2 and sets it into motion. This partition is therefore moved and drives with it the disk l3 at a speed equal to that of the plates M, II. Should now the port 59 be only partly closed by the cock 6|, the oil circulation from the chambers 81,82 toward the chambers 88, II is merelyi slowed down, this resulting in arotary sliding motion of the disk [8 with respect to the plates l. ll.

In the constructional form shown in Figs. 1 to 3, the passage of the fluid from the disk channel l8 to the disk channel I8 is closed off by shifting the cock 2| in the direction shown by the arrow 28 (Fig. '2). a

In order to permit the rotary motion of the driven shaft to be further transmitted, said shaft may be furnished with a pulley or any other suitable contrivance of conventional form (not shown).

Should the mouth 21- of the disk channel H be fully closed off, the driven shaft ll will revolve as fast as the driving shaft 2. In such case, direct drive may be obtained by bringing claws 28 splined on the driven shaft I (Fig. 2) into meshnel I8 is only partly closed, the oil can flow there through slowly on account of the resulting overpressure against the face It of the partition l2,

whereby the latter is moved and drives with it the shaft 5 but at a speed lower than that of the driving shaft 2.

The resultant rotary sliding action is the larger as the flow of oil is less slowed down. This enables an unlimited number of transmission ratios to be readily obtained in a most simple way.

In the modified constructional form shown in Figs. 7 to 10,- the driving shaft 2 is secured to a pair of semi-circular shell members 3|, 82 having facing surfaces so cut as to form walls between which is movably arranged a sector-shaped Partition 88 to which an oscillatory motion is imparted with respect to the central port 84, valve 22 governing flow from one side of partition 38 to the other. The power transmitter assembly thus built up forms a change speed gear box whose operation is substantially the same as that of the first constructional form as above described.

In Fig. 7 is shown, (by way of example, a reversing gear mechanism comprising a slidable clutch collar 85 splined to a driven shaft and movable into mesh with the clutch 86 of the bevel pinion 88 or clutch 31 of the bevel gear 38, an intermediate idler bevel gear 40 being constantly in mesh with the bevel gears 88 and 89. The bevel gear is carried by the shaft 5 as herein shown.

When collar 85 meshes withclutch 38', a direct p drive to shaft 5 is obtained, and when collar 88 is in mesh with clutch 81, drive shaft 5 will be driven in the opposite direction through gears 38, 40 and 88.

This power transmitter enables the ratio of the speeds of the two shafts which it intercouples to be changed. However, it does not fully trans mit the input power.

In contradistinction to this, a change speed gear box embodying the power transmitter according to the invention and as shown in Figs. 11 to 24 possesses the speed changing characteristics as above described and is adapted, moreover, to fully transmit the input power when the speeds of the driving and driven shafts are in inverse ratio to the capacities of the two chambers connected to the respective, shafts.

The power transmitter shown in Fig. 11 is made up of a pair of chambers 84, 68 having arcuate walls and different capacities, mounted for rotation on a tubular shaft 88 and having intercom,-

municationas will be described; hereafter.

- The smaller chamber as is defined by a pair bf shell members 81, 88 having walls so cut as to present .undulated faces between which is arranged a sector-shaped partition 88 movable parallel to the axis of said chamber 88 and to which is imparted an oscillatory motion relative'to the chamber center. Such partition 88 which ensures fluid tightness between the chamber walls is housed in a recess provided to that effect in a disk 18 rigidly carried by the tubular shaft 88 and revolubly housed in the chamber 84.

Inside the larger chamber defined by the two shell memlbers ll, 12 are accommodated a disk 18 and a partition I88 movably arranged between walls similar to those of the chamber 88.

Inside the tubular shaft 88is housed for longitudinalfmotion a cylindrical valve 14 which enables the rate of flow of the liquid between the compartments of one and the same chamber or of a pair of different chambers as well as the direction of circulation of the liquid betweenthe large chamber compartment to be adjusted.

In order to bring the cylindrical valve 14 to the gear ratio, highv gear ratio and reverse run, the

- displacement of said valve 14 is controlled by a rod 15 fixed by a key 18 to a ring 11 slidably mounted on the driven shaft I8.

Where the power transmitter is used as a change speed gear on a vehicle, the smaller chamber 88 of the transmitter unit is coupled at the left hand side end with the power or driving shaft 18 while its larger chamber is coupled at the right hand side end with the driven shaft 18. I

Should the engine of the vehicle be started while the cylindricafvalve H is in the position shown in Fig, 1 l. the vehicle cannot be set into motion because inside the chamber 88 which rotates together with the driving shaft 18 the liquid freely circulates from one face to the other face of the movable partition 88 through the channel MS of the cylindrical valve 14 (Fig. 12 and through channels 8|, 82 formed in the disk 10 the liquid circulation will be set up from the smaller chamber 84 toward-the larger chamber 65 through the side channels 88, 88 (Fig. 15) in the valve 14. The path followed by the liquid will be therefore as follows: channel 8| in disk in (Fig. 24), side channel 88 in valve ll, channel 90 in disk I8 (Fig. 15), chamber 66, channel 81 in disk 13, channel 88 in valve I4, and channel 82 in disk 10.

Owing to the reactive stress exerted by the liquid against the walls of the chamber 88 whose casing is mounted upon the driven shaft E8, the vehicle will be started and will take up a speed which will increase at the same time as the rate of flow between the chambers 84 and 65, i. e.

at the same time as the relative speeds between larger chamber 65 and smaller chamber 84.

ports II and to establish communication with the channels II, I2 in the disk II, direct communication of the liquid through the smaller chamber 84 will be cut off. The full quantity of liquid will flow through the larger chamber II owing to the provision of the side channels -II, II and will impart thereto a motion whose speed will be in inverse ratio to the relative capacities of both chambers I4, II.

It will be noticed that owing to the larger radius and the larger pressure surface in the larger chamber II, the energy is transmitted without any substantial loss.

In order to further increase the speed of the chamber II, the driven shaft II may be freed by shifting the clutch II in a direction reverse of that of the arrow II and the cylindrical valve 14 may be further moved in the same direction. When the ports I2 no longer register with II and 82 and side ports II, I4 are no longer opposite the respective ports of the channels II. II (Figs. 15 and 22) in the disk II, the liquid flow is cut oif intermediate the chambers I4, II.

After the liquid flow has thus been cut off, both chambers I4. II and the tubular shaft II revolve at the same speed. By moving the clutch 83 in a direction reverse to that shown by the arrow II, a direct drive is secured since owing to the intermeshing of the clutch parts II, II with the clutch parts 81, II respectively connected to the driving shaft II and the driven shaft II are coupled up. At that moment, the liquid pressure inside the chambers is equal to zero.

In order to obtain a reverse drive, the cylindrical valve 14 must be moved in the direction shown by the arrow II until the ports II, III assume the position opposite channels II and 82, respectively. The clutch II should be moved in the same direction to connect up the tubular shaft/I8 to the frame I'I.

When the ports 88 and III coincide with the channels 8i and I2 in the disk II, the liquid flows through the slanting channel III toward the side channel 89 formed in the opposite face of the cylindrical valve I4. Conversely the channel III is set into communication with the other side channel 88 through'the other slanting channel I02. The direction of the liquid flow through the chamber 85 is therefore reverse to its previous direction of flow. This change of flow direction involves a change in the direction of revolution of the chamber II with respect to its previous direction of revolution. The reverse drive of the vehicle fitted with such a power transmitter is thus obtained.

Assuming the cylindrical valve 14 to occupy the position shown in Fig. 11 (idle run position) and said valve to be brought to the position corresponding for example to the lower gear ratio and assuming, moreover, the driving shaft II to revolve in the direction shown by the arrow III (Fig. 24) the smaller chamber 84 will rotate in the same direction. As pressure prevails in the channels II, 88, II. the larger chamber is driven in the same direction.

Should now the cylindrical valve 14 be so moved as to bring the ports 88, III to the locations occupied by those of the channel II, the pressure will prevail in the channels II, II, II and the larger chamber will revolve in the direction indicated by the arrow II4.

It will be seen that the twin chamber change gear power transmitter as above described enables an unlimited number of gearing ratios to be obtained during which the powers of the driving l a cylindrical valve III.

and driven shafts are proportional to the speeds of said shafts. Moreover, said transmitter permits two gearing ratios, 1. e. two rates of speed to be secured, namely a direct drive, and a drive which is inversely proportional to the capacity of the two chambers.

The constructional modification shown in Figs. 25 to 37a is based on the same operational principle and is adapted to fully transmit the Power received for three set rates of "speed and to obtain an unlimited number of gearing ratios but with a decrease in the power.

In this constructional modification of the power transmitter there are provided a smaller chamber I20 (Fig. 25) and a larger double chamber Hi. The capacity of said larger chamber is split into a pair of compartments by a partition I22 held stationary by securing means such as dowel pins I2I.

In the compartment I24 are revolubly arranged a disk I28 and its movable partition I2I while in the other compartment I21 are revolubly arranged a disk I28 and its movable partition I28. These two disks are rigidly connected to a tubular shaft III in which is movably housed As shown in Fig. 29, said valve comprises a sleeve III surrounding a core III having a port I24 for idle running conditions and more or less elongated grooves providing direct or reverse communication between the compartment III in the smaller chamber I2I and the compartments I24, I21 in the larger chamber I2I. The channels III, III facing the larger chamber have a particularly elongated shape as well as those III, III in front of which are the ends of the channels I40, I in the disk I42 which drives the movable partition I41.

The channels I, I44 establish communication between the compartments defined in the smaller and larger chambers as shown in each particular instance by the detailed figures IIa, III: to Ila and I'Ib.

A power transmitter thus constructed is also provided with a conical member I45 whose axial displacement provides or fails to provide a connection between the chambers I2I, I2I and the toothed clutch I48 secured to the shaft III.

When shifting the cylindrical valve III to match requirements, a flow of liquid is established between the smaller chamber I20 and the two compartments I24, I21 of the larger chamber I2I or else such flow is reduced to the flow between the smaller chamber I 20 and one compartment of the larger chamber Hi. The partitioning of the larger chamber into a pair of compartments permits three ear ratios to be obtained and a full transmission of the input power to be secured. Such gear ratios are as follows: Firstly, a direct drive. Secondly, a gear ratio which is in inverse terms of the capacity of the chambers I20, I2i. Thirdly. a gear ratio which is in inverse terms of the capacity of the smaller chamber I2I with respect to that of one of the compartments in the larger chamber I2 I.

The operation of this power transmitter is substantially the same as the one of the transmitter shown in Figs. 11 to 24 with the exception that during operation with the upper gear ratio the extreme compartment I21 of the larger chamber I2I does not operate.

It will be understood that in order to obtain the upper gear ratio, the cylindrical valve III must be so shifted as to bring the line Ila-Ila of Fig. 25 to the location of the line IIa-IIa.

end surfaces, a channelled circular disk rigid The end "la 01" said valve then entirely projects from the port of the channels I32, l32a (Fig. 27) .in the outermost disk I28 oi the larger chamber flows without producing any eflect as in the smaller chamber I20 during idle run.

Therefore the capacity oi the larger chamber iii is reduced as it were by comparison with the capacity oi the smaller chamber I20. The speed or the driven shaft is consequently enhanced.

it willbe seen that a power transmitter as above described enables the several objects of the invention to be fulfilled and particularly the fol. lowing results to be obtained, namely:

(a) an unlimited number of transmission ratios between a driving shaft and a driven shaft:

it) three diflerent rates of speed or transmission ratios without any reduction of power:

t is) a selective reverse in the direction or rotaion.

Minor constructional details might be changed without departing from the scope of the sub- .loined claims.

What is claimed is;

i. ii power transmitter comprising in combination with a driving shaft and a driven shaft a casing rigid with the driving shaft and defining a fluid-containing chamber having a circular peripheral surface and slnusoidally curved parallei end surfaces, a channelled circular divider rigid with the driven shaft and so revolubly fitted in said chamber as to split it diametrically into a pair of communicating compartments, 9, ported partition slidably carried by said divider and tightly contacting the chamber nd surfaces to divide each compartment into a pair of communieating sub-compartments, primary valve means controlling the communication between the compartments through the divider channels, and sec.- ondary valve means controlling the communica' tion between the pairs oi sub-compartments on opposite sides of the partition through a port in the same.

2. A power transmitter comprising in combination with a driving shaft and a driven shaft a casing rigid with the driving shaft and defining a fluid-containing chamber having a circular peripheral surface and cinusoidally curved parallel with the driven shaft and so revolubly fitted in said chamber as so split it diametrically into a.

pair of communicating compartments mutually communicating through the channels of the dish and having a constant total volume a partition slidably carried at right angles through said disk and tightly contacting the chamber end surfacesto divide each compartment into a pair oi sub-compartments, each face of the partition having longitudinal ports interconnecting the subcompartments on opposite sides of the disk, the partition also having a. transverse port interconnecting its longitudinal ports, primary valve means controlling the sectional area of the disk channels. and secondary valve means controlling the sectional area of the partition.

3. A power transmitter as recited in claim 1 wherein said partition is formed of a plurality of interfltting members slidable relatively to each other through said divider.

4. A power transmitter as recited in claim 1 wherein said partition is formed of a plurality oi members slidable across said divider and slidably connected to each other-by interfitting tongues and grooves ior movement relatively to each other.

5. A power transmitter as recited in claim 1 wherein said partition is formed oi a pair or interfitting members slidable relatively to each other through a radial notch in said divider.

6. A power transmitter as recited in claim 1 wherein said partition is formed of a pair of Julia taposed members slidable across said divider, and formed with interfitting tongue and groove connections on their adjacent side faces and with ports on their outer side faces.

7. A power transmitter according to claim i wherein said partition is formed with ports in its side faces and said divider is formed with curved channels respectively connecting said ports with said primary valve means.

8. A power transmitter according to claim 1 wherein said partition is formed with ports in its side faces and said divider is formed with curved channels respectively connecting said ports with said primary valve means, and said ports are connected to each other by a crossport extending laterally across the partition, the eflective area oi said crossport being controlled by said secondary valve means.

"WINCENTY JASTRZEBSW.

transverse port in the 

